Bowl adjustment for crushers



Aug. 13, 1968 Filed March 16, 1965 F. M. ALLEN BOWL ADJUSTMENT FOR CRUSHERS 2 Sheets-Sheet 1 ATTORNEYS Aug. 13, 1968 F. M. ALLEN BOWL ADJUSTMENT FOR CRUSHERS 2 Sheets-Sheet 2 Filed March 16, 1965 INUENTOQ FEQNK M 4445M M87Ullu ATTO2NEV$ United States Patent 3,396,915 BOWL ADJUSTMENT FOR CRUSHERS Frank M. Allen, Whitefish Bay, Wis., assignor to Barber- Greene Company, Milwaukee, Wis., a corporation of Wisconsin Filed Mar. 16, 1965, Ser. No. 440,082 18 Claims. (Cl. 241-290) ABSTRACT OF THE DISCLOSURE The present invention relates generally to improvements in the art of crushing rock and ore, and relates more particularly to the provision of an improved device for rotating the bowl or concave of a gyratory or cone type crusher to effect adjustments in the position of the bowl relative to the crushing head.

Background of the invention Various types of crushing machines for the reduction of rock and ore have been heretofore proposed and are in common use. One of the most popular types of such crushing machines is the gyratory crusher. Briefly, a gyratory crusher embodies a rotary member or shaft carrying a crushing head mounted off center or eccentrically with respect to the axis of shaft rotation so that the head wobbles or gyrates within a surrounding concave bowl during crusher operation. Accordingly, the crushing action takes place in the gap between the gyrating crushing head and the bowl or concave.

In these machines, the particle size of the final product as produced by the crusher is dependent upon the size of the gap in the crushing zone which is defined by the space between the bowl and the head. Therefore, whenever it is desired to vary the particle size, it is necessary to change the dimension of the gap. In order to accomplish this, it is common practice to mount the crushing bowl or concave on the frame of the crusher in a manner which permits movement of the bowl relative to the crushing head.

While diverse means have been employed to permit adjustments to be effected in the position of the bowl, one of the most common expedients is to provide a threaded adjustment ring on the crusher frame and to form the crushing bowl or concave with a threaded flange engageable with the threads of the ring. Thus, the 'bowl is movable toward the crushing head to decrease the gap and particle size by rotating it in one direction Within the threaded adjustment ring, and it is movable away from the crushing head to increase the gap and product size by rotating it in the opposite direction.

In gyratory crushers which employ such threaded adjust-ment ring on the frame and a cooperating threaded flange or the like on the bowl, it is necessary to provide means for rotating the heavy bowl to effect the desired adjustments. Such adjusting mechanism must be capable of rotating the heavy and ruggedly constructed crusher bowl along with its attendant apparatus over the resistance of considerable friction and binding between the relatively movable elements. Furthermore, rapid and pos itive operation is desirable so as to eliminate costly and time-consuming delays and non-productive shutdown time. -In addition, the adjustment device must provide for effective rotation of the crushing bowl in both directions in order that the size of crushing gap may either be increased or decreased as required. Moreover, the adjustment mechanism must be safe in operation and rugged and durable in construction with a minimum of mechanical parts.

3,396,915 Patented Aug. 13, 1968 Summary of the invention It is therefore a primary object of this invention to provide an improved automatically operable mechanism for rotating the bowl of a gyratory crusher to adjustably position the bowl on the crusher frame in a most efficient manner.

Another important object of the invention is to provide an extremely simple, compact and durable bowl adjusting device readily operable by relatively unskilled personnel to rapidly and effectively rotate the bowl in either a clockwise or a counterclockwise direction to accurately position the same on the crusher frame.

Still another object of the invention is to provide an improved adjusting mechanism for rotating a crusher bowl to adjustably position the same on the crusher frame which is highly flexible in its adaptations and readily applicable either to existing installations or to new machines, and which is furthermore substantially trouble-free with a minimum of mechanical parts subject to fatigue and resultant failure.

A further object of the present invention is to provide an improved adjusting mechanism for gyratory crusher bowls which includes a hydraulically operated pawl automatically actuated at the will of an operator, to rotate an adjusting nut carried by the bowl, the pawl being pivotally or swingably supported in a unique manner whereby the need for springs or other mechanical means for returning the same to or from a given position is entirely obviated.

These and other specific objects and advantages of the invention will become apparent from the following detailed description.

The drawings A clear conception of the construction and operation of the bowl adjustment device embodying the invention and showing the same applied to and used in conjunction with a typical gyratory crushing machine may be had by referring to the drawings accompanying and forming a part of this specification, wherein like reference characters designate the same or similar parts in the several views.

FIG. 1 is a part-sectional side elevational view of a typical gyratory crusher embodying a bowl adjusting device of the present invention;

FIG. 2 is a somewhat enlarged fragmentary top view of the adjusting mechanism and the attendant portion of the bowl adjustment nut and showing the actuating pawl in one of its positions wherein it is approaching the end of its stroke just prior to reversal of the ram;

FIG. 3 is a similar fragmentary top view showing the pawl in another of its effective working positions near the commencement of its strokes;

FIG. 4 is an enlarged side view of the pawl and pawl guide with an electric switch operating device mounted thereon, a part of the pawl guide being broken away to also show the use of an adjustable friction drag for the pawl;

FIG. 5 is another fragmentary top view showing a similar actuating pawl but with the pawl guide modified to include a nut engaging locking portion and with the pawl friction drag in a somewhat different location;

FIG. 6 is another enlarged fragmentary top vie-w of a somewhat modified actuating pawl which may be used in the improved bowl adjusting device; and

FIG. 7 is still another fragmentary top view showing a further modified actuating pawl capable of being interchanged with the pawls shown in the preferred arrange ment.

Detailed description While the present invention has been shown and described herein as being especially adapted for usewith a gyratory crusher having a particular structural arrangement for the crusher frame, adjustment ring, concave bowl and adjustment nut therefor, it should be understood that the improved bowl adjustment mechanism may be advantageously applied to and utilized with different types of gyratory crushers, either with or without modifications, without departing from the spirit of the invention. It is also intended that the broadest possible interpretation shall be given to the descriptive terminology used herein, and it should furthermore be understood that itris entirely possible to utilize only a single pawl actuator rather than a pair of such actuators as shown and described herein.

Referring patricularly to FIG. l of the drawings, the gyratory crusher shown therein generally illustrates the type of crushing machine with which the present adjusting mechanism may be utilized to advantage. In this machine, the numeral indicates the annular main frame or base of the crusher which terminates at its upper edge in outwardly projecting flange 11. In turn, a concave supporting and adjustment ring 12 is seated on the frame flange 11, and this ring 12 is formed with internal screw threads 13. Adjustably supported on the main frame of the crusher is an annular crusher bowl or concave 15 having a radiating flange 16 formed with external screw threads 17 coacting with the threads 13 of the ring 12, the bowl 15 also being provided with a generally frusto conical inner liner 18 suitably secured thereto. Mounted eccentrically at the upper end of a vertical rotatable shaft 20 extending centrally within the frame 18 is a gyratory crushing head 21, and the shaft 20 and head 21 carried thereby are driven ina known manner by a suitable motor and belt drive (not shown) connected to a.

grooved pulley or sheave 22 which is, in turn, drivingly coupled with the lower end of the shaft 20. Thus, the eccentrically mounted gyrating head 21 cooperates with the frustoconical liner 18 of the bowl or concave 15 to provide a downwardly and outwardly flaring annular crushing chamber or gap 23.

In this type of gyratory crusher, the bowl supporting ring 12 is normally urged downwardly to seated condition against the stationary main frame flange 11 by an annular series of stud bolts 25 or the like having their upper ends seated against radiating portions 26 of the ring 12 and their lower ends carrying an annular reaction ring 27. Compressed between the flange 11 of the frame 10 and the reaction ring 27 carried by the studs 25 is an annular series of coil springs 28 which are retained under compression by the studs 25. Thus, whenever an uncrushable article such as a piece of metal or extremely hard rock or the like is deposited within the crushing chamber 23 during operation of the crusher, the springs 28 will become further compressed sufficiently to allow the concave or bowl 15 along with the ring 12 to move away from the fixed frame 10 and the crushing head 21 a distance sufficient to permit the foreign object to escape without damaging crusher parts.

As heretofore indicated, the particle size of the crushed material produced by the crusher is determined by the size of the crushing gap 23 between the bowl or concave liner 18 and the crushing head 21. Accordingly, if it is desired to change particle size, it is necessary to change the dimensions of the crushing gap 23. This is done by raising or lowering the crushing bowl 15 on the crusher frame 10 relative to the crushing head 21. In the crusher illustrated, the raising or lowering of the bowl or concave 15 is accomplished by means of the coaction between the screw threads 13 of the bowl supporting ring12 and the mating threads 17 of the bowl flange 16, the desired adjustments being effected by rotating the bowl 15. To facilitate rotation of the bowl 15 exteriorly of the crusher, an annular cap 30 is secured as by welding and/ or bolts (not shown) to the upper annulus of the bowl 15. This 4 cap 30 not only serves as a shield to protect the screw threads 13, 17, but it is also provided with an annular series of radiating ribs or lugs 31 which enables the cap 30 to also act as an adjustment nut for the bowl 15 as will hereinafter more fully appear. Thus, rotation of the cap 30 also rotates the bowl 15 which will accordingly be raised or lowered on the frame 10 by the coaction of the threads 13, 17.

In accordance with the present invention, rotation of the cap 30 and bowl 15 is accomplished either by one or by a pair of oppositely directed pawl assemblies 35, 36

or the like, each pawl having its respective shaft or body portion 37, 38 slidably received in a slide guide or cage 39, 40 or the like. The pawl guides 39, 40, are, in turn, each pivotally mounted as at 42, 43 respectively on a mounting plate44 or the like, and this plate 44 is secured to the crusher laterally adjacent to the adjusting nut or cap 30 as by means of upper extensions on selected ones of the stud bolts 25. Thus, with the pawl slide guides 39, 40 swingable about their respective pivots 42, 43, reciprocating movement of the respective pawls by means of actuating forces directed against the heads 46, 47 thereof at an angle to the longitudinal axis of their respective shafts 37, 38 will cause the pawls 35, 36 to swing so that the respective pawl heads 46, 47 selectively engage the lugs or ribs 31 of the cap 30 to thereby rotate the cap 30 and bowl 15 in an obvious manner, either clockwise or counterclockwise dependent upon which of the pawls is being actuated.

In the present instance, fluid pressure is used to actuate the pawls 35, 36. As shown, a pair of double-acting hydraulic ram units 50, 51 may be conveniently mounted on the plate 44 as by means of an upstanding angle iron bracket 52 or the like which is located radially outwardly of and between the pawl assemblies. With the cylinder end 53, 54 of each of the respective rarn units pivotally secured as at 55, 56 to the upright post or bracket 52 and with the extensible piston or plunger 57, 58 of each unit pivotally connected as at 60, 61 to the heads 46, 47 of the respective pawls 35, 36, the pawls may be selectively power actuated in an obvious manner by fluid pressure supplied alternately either to the ports 62, 63 on opposite sides of the piston in cylinder 53 or to the ports 64, 65 on opposite sides of the piston in cylinder 54.

To supply pressurized fluid selectively to the cylinders 53, 54, a suitable hydraulic circuit may be employed. As shown in the present instance, hydraulic fluid from a supply reservoir is pumped by a suitable hydraulic pump 71 either to the cylinder 53 via conduits 72, 73 or to the cylinder 54 via conduits 74, 75 as selected by an operator.

Automatic reciprocation of the cylinders that operate the pawl may, of course, be achieved in various ways, but as shown, a pair of electrically operated solenoid valves 76, 77 may conveniently be utilized for directing fluid flow respectively to the cylinders 53, 54.

The solenoid valves 76, 77 may be actuated by. means of an electrical circuit which includes a selector switch 80 interposed between the supply line 81 and lines 82, 83 connected respectively to the solenoids 84, 85 of the valve units 76, 77. Also included in the electrical circuit are a pair of limit switches 86, 87 operated respectively by the extension and retraction of the pistons 57, 58 of the hydraulic ram units to open and close the lines 82, 83 respectively. The solenoid valves 76, 77 are so designed that when the selector switch is moved to the off position, or when the electric current is interrupted, the flow of hydraulic fluid is automatically directed by the valves to position the hydraulic rams 50, 51 in their retracted positions in which the pawls 35, 36 are moved entirely away from the adjusting nut or cap 30. Thus possible damage to the adjusting mechanism is eliminated in the event the crusher bowl 15 and the adjustment nut 30 should tend to rotate while the crusher is in operation.

To operate the adjusting mechanism shown and described herein, the hydraulic pump 71 is first energized to supply power for the cylinder ram units 50, 51. The desired rotation of the crusher adjusting nut 30 and the bowl 15 is then selected by means of the selector switch 80. If the pawl limit switch contacts are closed, current then flows to the solenoid 84, 85 which shifts to the position directing flow through valve 76, 77 to port 62, 64 of the selected cylinder 53, 54 thereby extending the piston and rod 57, 58 connected to the respective pawls 35, 36. When the hydraulic ram is extended to its predetermined distance, the contacts open in the limit switch 86, 87, thus breaking the current to the solenoid 84, 85 which then shifts to the position directing hydraulic fluid to the port 63, 65 of the selected cylinder 53, 54 retracting the piston rod 57, 58. At the end of the predetermined retractinig stroke of the cylinder, the contacts in the limit switch again close causing the cycle to reoccur.

The recycling and resultant reciprocation of the piston rods 57 or 58 as selected by the operator in the manner thus described causes the selected pawl 35, 36 to reciprocate and simultaneously rock about its respective pivot 42, 43 and into and out of contact with the nut 30 and lugs 31 to thus rotate the nut and the bowl 15 attached thereto. This recycling action continues automatically as long as the power is on with the system energized as described, and to assure suflicient residual hydraulic power to retract the rams 50, 51 and thus withdraw the respective pawls 35, 36 entirely away from the nut 30 in case of electrical power failure, and accumulator 105 may be provided in the main hydraulic feed line 90. Thus, if the electric power is interrupted with either of the pawl actuating pistons in its power stroke, the solenoid valve will be returned to its normal ram retract position (valve 77 of FIG. 2) by the action of its respective return spring 106, 107 since the fluid in line 73, 75 is pressurized by the accumulator 105.

In accordance with customary practice, check valves 108, 109 are incorporated in the hydraulic feed lines from the pump to each cylinder in order to prevent feedback between cylinders. Also, other means to cause reciprocation of the pistons in the cylinders may be employed instead of the limit switches shown and described herein. Such means may comprise pressure operated valves or mechanically operated valves driven directly from the cylinder to achieve the same result. As shown, it is of course additionally desirable to incorporate an adjustable relief valve 110 in the hydraulic circuit in order to govern the hydraulic forces exerted and thereby prevent possible damage due to excessive forces.

In any event, the inventive concept involves the provision of one or more actuators suitably mounted for sliding and pivotal movement along with means of one kind or another operable on the actuator to simultaneously reciprocate and rock the same and thereby transmit radial and rotative forces to the crusher bowl. To cut down on cost, it is of course entirely possible and practical to use only a single actuating unit which may be interchangeably positionable selectively on either one of two pivot points so as to rotate the concave or bowl in the desired direction depending upon the mounting of the actuator. Furthermore, automatic operation may be dispensed with if desired, and the automatic devices such as the limit switches, selector switch and solenoid valves may be replaced by manually operated valves and a hand operated pump to thereby additionally lower the cost of the device.

Asshown in FIG. 4, the limit switch 86 (or 87) may be conveniently mounted as on a pedestal 112 or the like adjacent to the pawl assembly. In turn, the shaft of the pawl 37 (or 38) may be provided with a trip pin carrying bar 113 secured to the pawl 37 at its extending end as by a screw or bolt 114 and spacer 115 so that the bar 113 spans the pawl guide cage 39. The bar 113 therefore reciprocates with the pawl 37 and is guided between suitable bar guides 116 on the guide cage 39, the bar also being provided with a pair of spaced upstanding limit switch trip pins 117, 118 for actuating the switch 86 as the pawl reciprocates.

In this same view, a friction drag device for the pawl 37 is shown in detail. This friction drag may consist merely of a small compression spring or the like held captive between an adjustable set screw 121 and a disk 122 formed of bronze or other non-corrosive and wear resistent material and bearing against a side of the pawl shaft. The spring 120, set screw 121 and disk 122 are all confined within a threaded hole 123 in the guide cage 39, and more-or-less frictional resistance to reciprocable movement can be imposed on the pawl 37 by adjusting the set screw 121. This frictional resistance or drag results in more positive movement of the pawl device as actuated by its hydraulic ram and the pawl is caused to swing outwardly about its pivot and away from the bowl adjustment nut immediately upon completion of each stroke.

As illustrated in FIG. 5, the pawl assemblies 35, 36 may also be provided with a locking device if desired. In this case, an extension 92 is added to the end of one or both of the slide guides 39, 40 the extension 92 being so positioned as to contact the ribs 31 on the crusher bowl adjusting nut 30 and thereby prevent rotation of the crusher adjusting nut 30 during operation of the crusher while also positively limiting rotation of the adjustment cap or nut 30 while the pawl is on its return stroke.

It should furthermore be understood that the pawl assemblies may be modified as shown, for example, in FIGS. 6 and 7. In FIG. 6, the slide guide 94 is provided with a palr of spaced pins 95, 96 or the like and the shaft or leg of the pawl 97 is formed with an elongated slot or groove 98 slidably received by the pins 95, 96. Thus, the pins 95, 96 and the slot or groove 98 permit the same action as the pawls 35, 36 as described in detail. In FIG. 7, the swlvelling slide guide 39, 40 or 94 is eliminated entirely and is replaced by a pair of guide pins 100, 101 which may be fixedly mounted on the plate 44. In this arrangement, the pawl shaft 102 is also provided with a slot 103 whlch is slidably received on the pin 100, and the pin 101 cooperates with the edge of the pawl shaft to prevent displacement and/or overtravel.

Vanous modes of carrying out the invention are contemplated as being within the scope of the following claims particularly pointing out and distinctly claiming the sub ect matter which is regarded as the invention:

I claim:

1. In a crusher having a frame, a crushing head mounted in said frame, and a crushing bowl mounted on the frame and adjustable by rotation to form an adjustable crushing gap with the crushing head; means to rotate the crushing bowl to effect adjustments comprising,

an annular member rotatable with the crushing bowl and provided with an annular series of radiating proections; an actuator slidably and pivotally mounted on the frame and engageable with said projections; and

means operably connected to said actuator for reciprocating the same and for simultaneously swinging said actuator toward and away from said annular member and into and out of contact with the projections thereon to rotate the bowl.

2. Means to rotate the crushing bowl according to claim 1, wherein the annular member rotatable with the crushing bowl is a cap secured to the bowl and extending upwardly therefrom.

3. Means to rotate the crushing bowl according to claim 1, wherein a pair of actuators are provided, said actuators being swingable in opposite directions to selectively rotate the bowl either clockwise or counterclockwise.

4. Means to rotate the crushing bowl according to claim 1, wherein the actuator is in the nature of a pawl having an elongated shaft slidably received in a pivotally mounted guide member.

5. Means to rotate the crushing bowl according to claim 4, wherein the guide member is mounted for swinging movement about a pivot axis located laterally of the pawl shaft and the plane of reciprocable movement thereof.

6. Means to rotate the crushing bowl according to claim 1, wherein the means for simultaneously reciprocating and swinging the actuator is a hydraulic power unit pivotally mounted independently of said actuator.

7. Means to rotate the crushing bowl according to claim 6, wherein the actuator and the hydraulic ram operably connected thereto are mounted as a unit on a plate secured to the crusher frame laterally of the bowl.

8. Means to rotate the crushing bowl according to claim 1, wherein the means for simultaneously reciprocating and swinging the actuator is a power device controlled electrically in response to the movement of said actuator.

9. Means to rotate the crushing bowl according to claim 3, wherein the means for selectively reciprocating and swinging the actuators includes a pair of hydraulic power units and electric control means therefor responsive to movement of the respective activators.

10. Means to rotate the crushing bowl according to claim 1, wherein means is provided for creating a frictional drag on the actuator to resist sliding movement thereof.

11. Means to rotate the crushing bowl according to an actuator mounted on the frame for sliding and pivotal movement; and means independently mounted for swinging movement and pivotally connected said actuator for simultane ously reciprocating and swinging the same into and out of contact with said lugs to thereby transmit radial and rotative forces to the bowl through said lugs.

13. A bowl adjustment mechanism for a crusher according to claim 12, wherein the actuator is a pawl having a head engageable with the lugs and a shaft slidably contained in a pivotally mounted guide member.

14. A bowl adjustment mechanism for a crusher according to claim 13, wherein the means for reciprocating and swinging the actuator is a hydraulic ram mounted at one end laterally of the actuator and pivotally secured at its other end to the head end of the pawl.

15. A bowl adjustment mechanism for a crusher according to claim 13, wherein the guide member is provided with frictional drag means coacting with longitudinal edge of the pawl shaft to resist sliding movement thereof.

16. A bowl adjustment mechanism for a crusher according to claim 14, wherein the hydraulic ram is doubleacting and is connected to a pressurized supply source past an electrically operable control valve.

17. A bowl adjustment mechanism for a crusher according to claim 16, wherein the electrical system for the control valve includes a limit switch and means carried by the actuator for tripping said switch responsve to movement of the pawl.

18. A bowl adjustment mechanism for a crusher according to claim 13, wherein the guide member is formed with an integral projection swingable with said member to a position between adjacent lugs whenever the pawl is withdrawn. 7

References Cited UNITED STATES PATENTS 3,325,108 6/1967 Balmer et a1 241-290 3,341,138 9/1967 Allen 241290 3,133,706 5/1964 Mertz 24137 3,133,707 5/1964 Zimmerman 241--37 3,140,835 7/1964 Balmer 24l286 GERALD A. DOST, Primary Examiner. 

